Patent GB-1490148-A (GB)
Title: Underspeed actuator for hydrostatic transmission
IPC: B60K17/10
Filed: 1975-09-30
Abstract: 1490148 Hydrostatic transmission control CATERPILLAR TRACTOR CO 30 Sept 1975 [20 Feb 1975] 39935/75 Heading F2W [Also in Division G3] In a hydrostatic transmission for a tracked vehicle wherein the transmission ratio is normally adjusted by a manually controlled linkage 90, 88, 74 acting on a pump displacement adjusting servo valve 58, an override control includes an actuator 50 operated by an engine speed responsive pressure and carrying a pivot 226 of the linkage which, on overload indicated by a fall in engine speed, acts on the linkage to reduce pump displacement. The actuator 50 is responsive to the pressure drop across a throttle valve 40 in the delivery of an engine driven pump 32. A manual override valve 44 neutralizes the transmission by interconnecting lines 46, 48 transmitting the speed responsive signal to the actuator 50 and, on further movement, vents a line 128 to open a by-pass valve 127 between the transmission high and low pressure lines and permit a spring applied fluid pressure released parking brake to be engaged. The pump 32 additionally supplies servo pressure 72 to pump displacement adjusting servos 52, 66 and make-up fluid 42 to the transmission. Transmission components.-A pair of hydrostatic transmissions drive tracks on opposite sides of the vehicle and each transmission comprises an engine driven variable displacement swash-plate pump 14, 16 in closed circuit with a fixed displacement motor 18, 20. Each transmission is provided with a composite relief, replenishing and by-pass valve 94, 96. Pump displacement control.-Pump displacement is normally adjusted by manually rotating a rod 248, Fig. 6, carrying a lever 244 which is pivoted at 242 to a lever 240 which rotates about the pivot 226. The lever 240 is pivoted at 246 to a link 88 which is connected at its other end to a linkage 74 which adjusts a servo control valve 58 of the pump 14 and is connected by a further link 92 to a linkage 76 which adjusts a servo valve 64 of the pump 16. The linkages 74, 76 which are described in more detail in Specification 1,484,429 are biased towards a zero pump displacement position by spring means (not shown). On rotation of the rod 248 the lever 240 rotates about the pivot 226 and imparts movement to the rod 88 the magnitude of which depends upon the position of the pivot 226. The movement of the rod 88 acts through the linkages 74, 76 to cause equal displacement changes in both pumps 14, 16. Engine speed responsive override.-The engine speed responsive pressure drop across the throttle valve 40 is applied to opposite ends of the actuator 50 and acts on a piston 210 in position to a spring 216. The piston 210 carries the pivot 226 which, in the position shown, is aligned with the pivot 246 so that movement of the lever 240 imparts no movement to the link 88. When the engine is operating at its normal speed the pressure drop moves the piston 210 upward to its maximum extent. Corresponding movement of the pivot 226 in a slot 238 of the lever 240 causes maximum movement of the link 88 for a predetermined rotation of the lever 240. On overload the pressure drop across the throttle 40 is reduced and the piston 210 together with the pivot 226 move down to reduce the movement of the link 88 for a predetermined rotation of the lever 240 and thus reduce pump displacement. When the speed of the engine rises again the pump displacement is returned to its original setting. The rate of increase in pump displacement is limited by a throttle 254 in the line 48. In Fig. 7 (not shown) a spring is provided below the piston 210 to reduce hunting. Manual override.-The manual override valve 44, Fig. 3, comprises valve spools 160, 162 respectively biased by springs 172, 174 to the positions shown in which the spool 160 interconnects the lines 46, 48 to equalize the pressures at opposite ends of the actuator 50 whereupon the spring 216 moves the piston 210 to the position shown for zero pump displacement. In the position shown make-up liquid from a line 42 passes through metering slots 184 of the spool 160 to an exhaust 182. On initial upward movement of the spool 160 the exhaust 182 is blocked and pressure builds up in the chamber 170. The pressure in the chamber 170 acts on the end of the spool 162 to move the latter up and disconnect the line 128 from an exhaust 188. Thereafter pressure liquid is supplied through a throttle 194 to the line 128 to release the brakes and close the by-pass valve 127. On further upward movement of the spool 160 the connection between the lines 46, 48 is metered and finally closed to permit speed responsive operation of the actuator 50. In Fig. 9 (not shown), a single valve spool combines the functions of the valve spools 160, 162. By-pass and relief valve assembly.-The pressures in the transmission lines 22, 24 are applied to the end chambers 124, 100 of a valve spool 98, Fig. 5, to move the latter to one of its extreme positions in which it connects the makeup line 42 to the low pressure line and a relief valve 122 to the high pressure line. The spool 98 additionally connects the low pressure line to an exhaust line 110 to provide a continuous change of transmission fluid. The by-pass valve 127 comprises a plunger 140 biased by a spring 142 and transmission high pressure fluid admitted to the interior of the plunger through an orifice 138 to the position shown in which the by-pass is closed. On venting the line 128 a piston 130 releases a ball valve 132 whereupon the pressure behind the plunger 140 is released to vent at 144. Thereafter the make-up pressure 42 moves the plunger left against the bias of the spring 142 alone to open the by-pass. When the line 128 is repressurized the ball 132 closes the vent 144 and pressure build-up behind the plunger 140 closes the by-pass.